Circular-knitting machine



(No Model.) 8 Sheets-Sheet 1 E. R. BRANSON. CIRCULAR KNITTING MACHINE.

No. 553,277. Patented Jan. 21, 1896.

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E. R. BRANSON. CIRCULAR KNITTING MACHINE;

No. 553,277. Patented Jan. 21, 1896.

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E. R. BRANSON. GIROULAR KNITTING MACHINE.

No. 553,277. Patented Jan. 21, 1896.

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E. R. BRANSON. GIRGULAR KNITTING MAGHINE.

Patented Jan. 21, 1896.

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E. R. BRANSON. GIRGULAR KNITTING MACHINE.

No. 553,277. PatentedJa n. 2 1, 1896.

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E. R. BRANSON. CIRCULAR KNITTING MACHINE.

No. 558,277. Patented Jan. 21, 1896.

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E. R. BRANSON.

CIRCULAR KNITTING MACHINE. No. 553,277. Patented Jan. 21, 1896.

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EDVIN R. BRANSON, OF PHILADELPHIA, PENNSYLVANIA.

CIRCULAR-KNITTING MACHINE.

SPECIFICATION forming part of Letters Patent No. 553,277, dated January 21, 1896.

' Application filed May 5, 1888- Serial No. 272,967. (No model.)

To all whom it ma concern.-

Be it known that I, EDWIN R. BRANSON, a citizen of the United States, residing in the city and county of Philadelphia and State of Pennsylvania, have invented certain new and useful Improvements in Circular-Knitting Machines; and I do hereby declare that the following is a full, clear, and exact description of the same.

Prior to my present invention knittingmachines of the class known as circular have been provided with mechanism for simultaneously lifting or throwing out of gear with their actuating-slots in the cam-cylinder a prescribed numbergenerally one-half of the needles preparatory to turning the heel or toe of a stocking, during which operation the needles thus withdrawn retain their loops passively, while those not so withdrawn are actuated and knit'as usual, the cam and needle cylinders being,however,at such times reciprocated instead of revolving continuously in relation to each other as they ordinarily do when engaged in producing the tubular web which constitutes the leg and foot of the fabric. These machines have, moreover, been provided with mechanisms by means of which the terminal needles of the row or series of those that do remain in action during the relative reciprocations of the needle and cam cylinders when turning are alternately and individually put out of operation, in order to effect the goring or narrowing of the web; also with other mechanisms by means of which the number of needles finally remaining in action can be augmented one by one, as it were, conversely bringing back into gear the terminal needles of the row or series which have been, as above mentioned, put out of gear, this being in order to Widen the fabric.

Now the chief object of my invention is, in rendering the Whole operation of the machine automatic, to establish a more positive connection and interaction of the parts, not only between the primary parts constituting the knittin g-m achine proper, but also between themand those which may be designated the secondary parts --VlZ., the former or pattern wheels and the turning, narrowing and widening ancillary attachmentsso that the whole may beunited into a wellconstructedlight-runningmachine. Subsidiary to this it is my object to adapt and provide not only special and suitable mechanism for carrying out the individual features of this improved machine, but also to combine and mount the moving parts in a frame calculated to give an orderly and simple distribution to these various component devices, together with improved mechanisms for controlling their connection with the motive power.

In addition, my further objects are, in carrying these improvements into practice, to devise and construct an improved mechanism for reciprocating the moving cylinder, and preferably so as to impart a varying angular velocity to said cylinderviz., a slow movement prior to and just after each reverse; to combine the same with an improved clutch mechanism for controlling said circu lar reciprocations of the moving cylinder, whereby it shall be started or stopped without unnecessary lash or lost motion, and always from a constant or fixed point in the relative movements of the main driving parts as they describe their functions; to devise and construct an improved controlling connection between the former-wheel train and the driving mechanism, so that the whole machine may be normally brought to rest upon the completion of the prescribed stocking or seek; and also so that during certain periods of rest occurring between the continuous and the reciprocating circular motions of the cylin ders in the head of the machine said former-wheels and secondary cam-train shall be brought automatically into operation; to provide suitable mechanism therefor, and to disconnect and arrest the action of the same when, the several ancillary mechanisms having been put in train, they are, in their respective turns, to be Withdrawn therefrom preparatory to the machines resuming its ordinary continuous tubular knitting of the leg or foot, as well as in combining and connecting with the primary parts of the machine those mechanisms by which the secondary operation of turning, narrowing, and widening are accomplished in such a way as to adapt them to perform and repeat in substantially the same way and order their several functions when knitting a foot and toe, re-

spectively, as they originally performed them in the substantially similar duty of knitting the leg and heel; to provide improved mechanisms for carrying the same into practical effect; to construct the head of the machine in such a way that while the needle-cylinder is normally fixed and secured to a chuck or seat it may readily be detached, and, if need be, replaced by one adapted for finer or coarser work by having a greater or lesser number of needles, &c. and to devise and construct suitable mechanism therefor.

Lastly, my object is also in setting forth the specification for the above as a whole to at the same time describe and secure certain novel improvements among said several devices and mechanisms, which, while they may be taken as complete in themselves, are yet so far ancillary in making the specific machine described automatic that they may seem to have lost their distinctive characters as novel and useful featuresin otherforms of construction were it not for this mention of my purpose of securing them in that aspect and the subsequent claims which aim at that end. Circular-knitting machines of this class(in which a hollow cam-cylinder jackets a'concentr'ically enveloped needle cylinder having the above-described alternate, continuous, and reciprocating circular motions, whereby the knitting-needles are each in its own guideslot re'ciprocated vertically by the engagement of their heels or offset lower ends in the slots of the cam-cylinder) being well understood, only as much of one of them provided with my above-mentioned improved devices is set forth and shown in the following description and drawings as serves to describe, distinguish, and connect therewith my invention; and in the light of that qualification, reference now being had to said accompanying drawings, forming a part of this specification, in which similar letters of reference indicate corresponding parts throughout all the figures, they will be found to illustrate the mechanism by which I have in practice attained the above-recited objects with the most useful results.

Figure 1 is an elevation of whatl designate the back of a circular-knittin g machine provided with my above-mentioned improvements throughout. In this view a portion of one of the legs X of the stand is removed in order to show the structural relation of the reversing-geans clutch, of which hereinafter. Fig. 1 is a detail view showing a modification of the driving mechanism in similar elevation. Fig.2 is an elevation of the driving end of said machine, upon which there is carried the cylinder-reciprocating mechanism. It shows the parts external to the adjacent leg X of the stand, as well as an end elevation of the secondary or external cam-train and formerwheels, together with the preferred relative distribution from this point of view of these two mechanisms not only to each other, but also to the vertical head of the knitting-machine. For. the sake of clearness, however, the driving-gear 'of the secondary cam-train and the main spur-gear of the continuous circular cylinder-rotating device are chiefly given in broken lines. A portion of the circular segment-rack U, with its intermeshin g pinion U,is likewise thus represented; also one of the cams E, with its bent actuating rock-arm e. Other parts, however, are not shown, as they, for the most part, lie back of, coincide in outline with, or otherwise would tend to confuse those already represented. Fig. 2-" is a detail viewshowing a modification of the mechanism for producing reciprocatory circular motion. Fig. 3 is a plan view, on a larger scale, of the machine, without indicating the legs of its stand. It shows the preferred distribution of the table, cylinder-head, secondary cam-train, and reciprocating mechanism. In this figure, also, the principal parts underlying the table T are indicated in broken lines, the more minute detail being reserved for other figures and descriptive matter. Fig. 4is a rear elevation, partially in section, of the cam, cam-lever, and clutch mechanism governing the above-mentioned relative movements and temporary arrests of the needlecylinders rotations. Fig. 4 is a detail view of a feature shown in Fig. .1:- Fig. 5 represents a partly-sectional end View of a portion of the structure shown in Fig. 4, also showing a convenient method of attaching lockingpawls for opposing the ratchet-wheels W ll, shown in Figs. 2, 7, and 8. Fig. 5 is an isometric view of the clutch, disks, and headlocking device. Fig. 6 shows a detail of a portion of the cam and slide-rod, with thrusting-lever for said clutch, as seen in plan. Figs. 7 and 8 are fragmentary views of the details of the devices for actuatingthe secondary cam-train and former-wheels in end and rear elevation, respectively. Fig. '7 is a perspective View, shown fragmentary, of a modification of the secondary cam-train. Fig. 8 is a side elevation, on alargerscale, of one of the wheels of the modified cam-train shown in Fig. 7 Fig. 9 is a vertical sectional elevation of the cylinder-head and miter-gear actuating mechanism,taken on the central line indicated by the dot-and-dash lines in Figs. 10 and 11. Fig. 9 shows one of my detaching wedgelugs of which hereinafter. Fig. 10 is a plan View of the bottom of the needle-cylinder. This View in connection with Fig. 9 is especially adapted to show the spring-stud device by which I render the needle-cylinders not only normally securely fixed to their seats, but also, on occasion, readily detachable as well as interchangeable. Fig. 11 is a plan view of the top of the cam-cylinder, showing my improved needle-lifting rest and compact automatically-operated cam-train, for which purpose the needle-depressor attachment is removed. Figs. 12 and 13 are vertical sectionalelevations of the two halves of said camcylinder, taken on the dot-and-dash line of Fig. 11. Fig. 14 is a side elevation of the camcylinder, showing the external detail of the mechanism for lifting out of gear a number of needles simultaneously preparatory to turning as aforesaid. Figs. and 16 are respectively a side elevation and a plan of a fragmentary detail of the mechanism for lifting out of gear individual needles for narrowing. Figs. 17 and 18 are, in relation to the cam-cylinder, respectively external and internal views of the mechanism for changing the length of stroke of the needles in their passage through the cam-train, forming an auxiliary tension. device. Fig. 19 is a side elevation of the mechanism for throwing a large number of groups of the needles simultaneously and automatically back into gear preparatory to the resumption of continuous circular knitting. Figs. 20 and 21 are frag ments respectively, external and internal, of the cam-cylinder provided with the mechanism for returning individual needles at each reciprocation of the needle-cylinder during the operation of widening. Fig. 20 also shows, as do Figs. 14 to 19, (saving Fig. 18,) inclusive, the cam-wheels'and cam-levers of the secondary or external cam-train which throw their respective mechanisms, at designated intervals, in or out of gear. Fig. 20 is an isometric projection of a portion of the str ucture shown in Figs. 20 and 21, having chief details offset, the point of view being approximately opposite the point of view from which Fig. 21 was taken. Fig. 20 is a similar view of one of the depressor-tumblers with the spring (1 and screw 19 therefor. Fig. 22 shows a detail of the cam and rider forming automatic belt shipper-bar actuating devices. Fig. is a representation of a vertical side elevation of the internal structure of the cam area of the cam-cylinder developed upon a plane, showing details of the cams, and indicating in the dot-and-dash line the normal path of the needles heels when passing from left to right through the cam system as shown. Broken lines indicate certain movements described and positions occupied by the needlelifter levers and the swinging nose of the central depressing-cam when knitting continuous tubular Web. The dotand-dash outlines designated 07. 11 01 are positions assumed by the tumblers n a when engaged in narrowing or gorin g the web, as hereinafter described. Fig. 24 is a plan view of said area of the cam-cylinder, showing detail. Fig. 24

. shows the form of needle best adapted to work in conjunction with the devices herein described and illustrated. Fig. 25 is a representation of a modified continuous tubular stocking fabric which the machine herein described can be adapted to produce. Fig. 26 shows an individual stocking-blank when severed and shaped from such continuous fabric as is shown in Fig. 25.

In the drawings the legs X X, hanger X table T, brackets or journal housi'ngs O O, and cross-bars O Z together with the pawlbearing lug N, constitute the frame proper of the machine, the whole being rigidly secured together and carrying, in cylindrical bearings 50 m m m of the leg X and hanger X parallel cylindrical shafts S S, of which S, being the power driving-shaft, is preferably fitted within its bearings with a fast beltpulley WV, (provided near its hub with a project ing tappet or stud 10,) a corresponding but loose pulley W, and fast spur-wheel V, and outside of bearing 00 there is secured to this shaft in the construction shown a crank 5, provided with a crank-pin p pivotally connecting therewith one end of a connecting-rod s, the other or outer end of which is provided with a knuckle s and pivotally connected by a pin 13 with an upright rock-arm R. The lower end of this arm is also pivotally connected near the foot of the leg X by a pin p passing through its eye 7', and preferably kept clear of the stand by a washer '1' (see Fig. 1,) while the upper end of rockarm R, extending above the summit of the circle described by the crank 8', ends in another cylindrical eye through which a pin 19 passes and serves, by means of the knuckle '1 to connect it pivotally with a drag-link 0', the other end of said link being pivoted by a pin 19 to a circular segmental rack U, (preferably of the general form and contour shown in Figs. 1 and 2.) This rack is likewise pivoted upon a trunnion or boss formed on the outside of the leg X by a pintle P, so that the teeth of the rack, which are, as indicated in Fig. 1, out upon the periphery of its arc, gear with a pinion U, of which hereinafter. The rack U, like the rock-arm R, together with all the moving parts immediately connected therewith, is adapted to vibrate or swing in vertical planes-that is to say, substantially at right angles to the axes of the drivingshafts S S. These parts may be dispensed with and a slider=crank substituted, as in the mechanism shown in Fig. 2 wherein U has a rigid middle member provided with a radial slot in which the crank-wrist of the crank s is engaged and operates to vibrate said rack about the pivot P and drive the pinion U with a reciprocatory circular motion. This is a modification, however, which involves a sacrifice of the even angular motions of the former, being, as is well known, productive of a reciprocatory motion swifter in one direction than in the other. Otherwise it is equally practical in combination with the remaining mechanism.

The shaft S is provided between its bearings with a loose pinion-wheel V intermeshing with the spur-wheel V fixed to the shaft S. Between said pinion and the bearing 00 it carries a face-plate or disk V divided into two flanges of difierent diameters bya peripheral annular groove '0 said disk being provided with a slot or keyway lengthwise of and in its eye, whereby the disk, engaging on a suitable key 5 either integral with or driven into a seat in the shaft S, as shown in Figs. 4 and 5, is prevented from revolving inde pendently of but remains free to move endwise along said shaft between the pinion V and bearing as, motion of this latter sort bein g occasionally communicated to V by means of the thrusts offered it through the straddling leg Q) of a U-shaped slider-piece U which is adapted to ride loosely in said groove 11 The shaft S is equipped, preferably outside the bearing with a substantially similar disk U provided with a corresponding groove 11/ and a keyway for a similar key fixed in shaft S. The adjacent pinion-wheel U, like its fellow V, is secured from motions endwise of the shaft S, upon which it is carried, either by means of its respective keys end 5 and a plain collar or preferably by such a collar as either 5 3 respectively. (See outlines thereof in Fig. 5 and more fully in Fig. 4.) Said collars are fixed to the shaft S and provided with flanges n v, respectively, to each of which are secured by screws S and steadypins S two or more circular segmental flan geclips S of the character best seen in Fig. 4. These clips being adapted to engage in annular grooves formed in the hubs of the pinionwheels U V serve to maintain them loosely as regards radial motion, as .well as in their working positions, without rubbing against the ends of their keys.

The inner sides of said pinion-wheels are further provided each with a hole a 0 adapted to engage and register with studs P P projecting equal distances from the ad joining sides of their respective slider-disks. One of these disks is also formed with a slot or gap J in the rim of the flange which carries said stud, the width of said flan ge being equal to the projection of said stud; and, adapted to work in connection therewith, there is secured to the bearing 00 a fixed finger J, so formed and located as to admit of the disk which has this gap to pass its inwardly-pointing finger-tip j, which is the c011- verse male part of said gap in form and dimensions, laterally along the shaft S only when they two viz., the gap J and fingerpoint-j are in radial alignment.

The slider U has a suitable hole(represented in dotted lines in Fig. 4:) through its connecting-body which, save for the spiral springs Q,

would permit it to freely slide on a bar S which, lying with its axis parallel to the shafts S S, is itself also adapted to slide endwise through suitable eyes formed in lugs ti,bolted to the under side of the table T. Said slidebar S is provided with certain abutments, as the washers t e U7 and pins p 13 p (shown in Fig. 4,) whereon the spiral springs Q, Q and Q with which it is helically wrapped in part react. It is also further provided with another abutment preferably made adjustable, as by the jam-nuts i t? and washer 0 Fig. 6, for the purpose of opposing the adjoining horizontally-swinging end of a camlever composed of two diverging arms A a, (see Fig. 6,) the swinging end of the longer of which, being preferably crotched and provided with disks a a adapted to embrace the shaft S*, as shown in Figs. 5 and 6, permits this lever to lie practically in the same general plane as the axis of the slide-rod S", the whole lever A a being pivotally connected to the table T (see Fig. 3) on a downwardlypointing pivot-pin P The pivot P is conveniently form ed, as shown in Fig. 5, with a main cylindrical shank terminating at its lowest extremityin a flat flange or head, which serves as a support to the lower side of said levers eye, after passing through which said pivot is enveloped freely in a tubular washer or sleeve p reaching to the adjoining under surface of the table T, through which the pivot P then passes with a reduced diameter of stem, and its shoulder, banking against bottom of table T, establishes the relative distance therefrom of the pivots above-mentioned head, and, taking advantage of a protrusion of said stems upper end, I secure here to the upper side of the tableT, by means of a screw-thread and nut on said pivot, as shown in Fig. 5, a hingebearing lug-piece N adapted to carry pawls P P which, extending outward beyond the back of table T, engage upon and lock the ratchet wheels V \V against accidental back slidings. (See Fig. 2.) Thenceviz., from P the shorter arm a of this lever passes and lies across in rubbing contact with the face of the secondary cam-wheel A, in which position the spring Q being normally under compression, is adapted to maintain it. Thus these two thrusting agents, in conjunction with the above-described gap J in the disk V and the finger J bolted to the side of the bearing 41:", as above described, and shown in Fig. 5, define the position of the stud-bearing clutch-disks V U in relation to the pinionwheels V U and their respective driving spur-gears, as is hereinafter more fully set forth in the narration of their mode of opera tion.

It will be merely pointed out at this stage that as the reciprocating rack U and the revolving spur-gear V are concurrently in motion during all operations of the machine the connections in and out of gear between them and cylindershaft S, which this clutch mechanism effects, take place when the pinion about to be engaged is already moving in the direction in which the cylinder driving-shaft S is to be itself then driven in. By this means lost motion is avoided between the intermeshing gear-teeth of the actuating spurs and pinions at the moment of beginning their actuating duty.

The spur wheel V and the reciprocating rack U serve, when one or the other is con nected through the gear-wheels V U on the shaft S to that shaft by the clutch, to impart to the shaft S corresponding motions; but as a great variety of mechanical equivalents may be substituted for a spur-wheel or a reciproeating rack,and also as many suitable clutches could be substituted for the one specificallyshown, I do not wish to be considered as limiting myself to the particular form of connections here shown.

Said cam-wheel A is fixed to a shaft S carried in cylindrical bearings o 0 (see Fig. 3) of dependent arms projecting from and forming parts of the brackets O 0 respectively; The aXis of this shaft liesparallel to that of shafts S S, and carries within its bearings what I have designated the former-wheels or secondary cam-trainviz., the cam-wheels B, C, D, E and F. Also upon a projection of shaft S extending outside the bearing 0 there are fixed the ratchet-wheel W (provided with occasional higher teeth, as Vt in Fig. 7 and the sliding-clutchscam-wheel A; also, between these a loose or idle ratchet-wheel V provided likewise with occasional higher teeth, as Vt, and, journaled upon a suitable eye, a bent-armed pendulous lever in, (see Figs. 1 and 2,) of which the dependent lower end is adapted to gravitate and rest normally against the front side of the power-shaft S, (see Fig. 2,) as well as within the range of the above-mentioned tappet to, while above said eye it extends upward and is provided on its side adjoining the ratchet-wheels \V" with a pin 19, Figs. 7 and 8. Upon this pin are pivoted pawls P P, provided with upwardly-extending lugs, the ends of which being formed oblique are provided with detents or notches u in, into one or other of which the hooked edge of a curved platespring 10 is adapted, on occasion, to register and engage. Said spring is secured to a convenient right-angled offset 20 in which the oscillatingtappetleverw here preferably terminates. In other cylindrical bearings 0 0 (see Figs. 1, 2 and 3) in the brackets O 0 there is journaled parallel to the shaft S a rock-shaft S Also in journals 0 0 paralleling and almost immediately over the former there is a second rock-shaft Both of these rock-shafts, itis to be noted, lie between the shaft S and the cylindenhead H I. (See Fig. 2.) Upon these shafts are carried rock arms or levers adapted to come into contact with and play over and be actuated by the cantbearing peripheries of the wheels B O D E F, as follows, viz:

First. A depending arm 1), preferably of the form and contour best observed by taking Figs. 3 and 14 in conjunction, is fixed to and points downward from shaft S. An off set I) in its lower end lies normally in contact with the periphery of cam-wheel B. Rigidly connected with arm 1') by the shaft S are two other inwardlypointing lever-arms 12 If, to the swinging extremities of which is secured a bridle B, loosely girdling the opposite eX- terior (front) wall of the cam-cylinder H. Said girdle is provided with screws b b",which project not only through it but also pass loosely through ports Z9 b in the cam-cylinder H, and thence extend toward and are screwed fast to a detached semicircular vertically-movable needle seat or rest B as clearly shown in Figs. 11 and 13. Also upon the periphery of the wheel B there is formed a cam or buffer 19 preferably of the profile shown in Fig. 14.

Second. Adjoining arm I), and loosely pivoted upon the rock-shaft S by a suitable journal 0'', arms 0 0 project, respectively, to the front and rear. Of these a is the heavier, and preferably provided with a friction-wheel c, which, being at a proper place for that purpose, reposes by gravitation upon the adjoining cam-wheel O, which is provided with peripheral high and low levels a 0 0 as shown in profile in Figx15. Otherwise the outer arm, a, of said lever maybe kept in contact with said cam-wheel under the constraint of a compressed spiral spring 0 ex tending between the upper side of arm a and the cross tie-rod O, as shown in Fig. 1. The inner extremity of the arm 0 is provided with a bent whisker 0 the ends of which, after spanning a proper angular distance on the cam-cylinder 11, enter the same loosely through suitable port-holes c 0 Figs. 11, 15 and 16, and form seats, as hereinafter described, for the narrowing-needle lifters.

Third. Next to cam-wheel 0, upon shaft S there is fixed a cam-wheel D having a depression (Z in its otherwise unbroken circular periphery, as shown in side elevation in Fig. 17. Over this a rock-lever loosely pivoted by asuitable eye about the shaft S and composed of arms d 61 likewise lies and plays. Of course the outer arm, (1, has substantially similar equipments of friction-wheel and either spring or gravitation means of contact with cam-wheel D as the lever c and cam C last mentioned had; but the inner arm, (Z forks near the wall of the cam-cylinder and passes loosely through the same by openings or ports, as shown at (Z (Z in Figs..17 and 18, the projecting inner ends thereof being provided "with downcast stitch-cams IN N of whichhereinafter; and between cams N N I locate the nose of the downward-pointing V- cam N, preferably provided with a swingpoint or switch n, as shown in Figs. 12 and 23.

Fourth. Fixed to the shaft S is another camwheel E, provided with a projection or boss (shown at a Fig. 19) on its otherwise circular periphery, and upon E the buffer-like lower end, 6, of rock-arm 6 plays. The upper end of said arm is rigidly secured to the rockshaft S from which shaft, and at right angles to its axis, two other rigidly-fixed leverarms e 6 project under the upward constraint of distended spiral springs q, as shown in Fig. 2, and pass inward over the cylinders H and I. The ends of said arms, which in plan View lie, as it were, tangentially to the sides of these cylinders, are united by a thin flat plate e Figs. 3 and 19, preferably of such an outlineand size that it shall, during its vibrations, overlie .the full number or more IIO of needles which the sliding rest B above mentioned is calculated to raise or lift, as hereinafter described.

Fifth. A cam-wheel F is fixed to the shaft S and provided with high and low levels, the surfaces f f whereof are simply arcs described with radii of different lengths, f" f and joined to each other by easy slopes. In contact therewith, and in manner substantially similar to that of cams O and D with their respective lever-arms, there is another rock-arm f, the inner part f of which, as shown in Figs. 3 and 20, is fashioned into or provided with a fixed curved whisker, the end of which registers with and engages loosely in a slot f in a backwardly-swinging forked flap-piece F hinged at its lower extremities h 72 to projections h" h on the adjacent exterior rear wall of the cam-cylinder 1-1. This is preferably so that the center of form of this flap F is approximately opposite the center of the cam system of the cylinder H.

Upon the upper or cross member of flap F there are carried inwardly-projecting lugs F F to the flat inner faces of which pivotscrews 19 19 support pendulous needledepressor tumblers F F, which when the flap F is up in contact with the side of the camcylinder hang downward within the same and alternately present their notched or detent bearing lower extremities in the path of the offset heels of such of the knitting-needles as may be elevated out of range of the slots of their actuating cam system into their nonacting level-to wit, the dot-and-dash line of Fig. 21. Spring-catches for these needle-depressor levers are indicated in Figs. 20 and 21 at g (1 wherein 71 77. also represent raised shelves or seats fixed to the rim of H, upon which F F repose when retracted. The whole attachment in its function, save for the novel automatic connecting device and the fashion and simplification of the depressorlevers and their retaining spring-catches, is one which operates,when in action, to the same end as the needle-dropping mechanism of kindred nature fully described in the United States Letters Patent No. 333,102 heretofore granted to me. Again, outside of the bearing 0 the shaft S extends and carries fixed upon it a wheel Z, Figs. 1, 3 and 22, the otherwise continuous even circular face of which is provided with a projection or stud 21, having oblique faces, as shown in Fig. 22, while between said wheel Z and the bearing 0 there is threaded on the shaft S by an oblong hole 5 a fiat plate Z, provided on its upper part with a stud .2 projecting at right angles over and resting upon the periphery of said wheel, whereon it rides idly save only when the same may in the course of its revolutions bring the cam-stud z into contact with it, as hereinafter described. The lower extremity of the plate Z is also connected with or formed into a crooked depending rod [53, which, passing through a suitable bridle or guide 2, is pivoted to a shipper-bar Z This bar passes horizontally across the legs of the machine-viz,

from X to X in Fig. 1and is provided with slots 2 2 adapted to allow said shipper-bar to slide endwise under the heads and along the stems of two shoulder-screws .2 .2 which, passing through these slots, are screwed at suitable intervals into an underlying fixed cross-bar Z Of these slots it is to be noticed that the one nearest the rod after extending for a distance, preferably about equal to the width of the driving'belt, in a straight course parallel to the axis of said shipper-bar, thence extends in a zigzag having angles .2 .2 2' &c., forming, as it were, a capital letter W, sloping generally in the direction of the slot 2 while the other slot e is simply an elongated right-angled parallelogram upon which the shipper-bar can either slide endwise, as above described, or else, if swung in a vertical plane, oscillate and pivot. The shipperbar Z is further provided with a downwardlyprojecting fork .2 adapted to guide the driving-belt to the belt-wheels IV \V in the usual way, while to and between the side or tine of said fork nearest leg X, and to said leg X, there is attached, under tension, a spiral spring L. The whole is shown in Fig. 1 in the position assumed at the outset of the knitting operation, where the screw 2 being engaged in the terminal angle of the zigzag continuations of slot e maintains the shipper with the fork 2 opposite to the fixed or driving-belt wheel IV despite the sidelon g pull of spring L.

Passing now to the head of the machine itself, Fig. 9 shows the method I prefer to employ in attaching the same to the table T viz, by means of two annular flanges. One, H, projecting at right angles to the shell of the cam-cylinder, is fastened by screws T to the table T, the other, H secured to the table T by means of suitable screws T fitting in holes The other, H passing downward through a suitable circular hole therein, is provided on its lower face with three or more tapped holes h, 850., into which screws h, 850., provided with inwardly-proj ectin g clip-pieces kg, 850., are screwed and support the annular chuck orcylinder socket I, so that it may revolve freely in its corresponding annular chamber it formed for that purpose in the lower extremity of the cam-cylinder II. Said socket 1, extending downward, terminates upon its lowest outer periphery with a mitergear 11, adapted to intermesh with and be driven by the teeth of the miter-gear 5- carried upon the shaft S. Internally, socket I is chambered out into a right-angled annular chuck-seat vi, into which the needle-cylinder I is adapted to fit snugly. I lock the needlecylinder in position by means of the following device: Holes 2' t are formed radially and preferably diametrically opposite each other in the side walls of said seat. I also secure to and near the base of the inner wall of the needle-cylinder I a curved spring I as by the screws indicated at m m in Fig. 9. The ends of said spring extending more than one hundred and eighty degrees and being of such a set that they may normally press against the adjoining shell of the cylinder I are pro vided with outwardly-proj ectin g studs 271 171 which pass freely through holes 1' 2' registering therewith, and pierce the shell of cylinder I. The length of the studs m m is such as to allow them ,when forced outward by the spring I through the shell of the needle-cylinder I, to project into the holes 1 i in the socket I, with which they also register and normally engage, but from which they can on occasion he disengaged and withdrawn by means of two downwardly projecting pull lugs M M. These I preferably make of thin strips of metal inserted respectively between the adjacent wall of the shell I and the respective bearing ends of the curved plate-spring 1 where they are' normally maintained pushed fiat against said wall until such time as they may be drawn farther down. (This drawing down, it is to be noted, forms no part whatever of the duty of the machine so far as knitting is concerned, but is only for the purpose of either putting in a needle-cylinder when assembling the machine, or else in order to change one needle cylinder for another; which, being desired to be done, said lugs are pulled down by hand until their involuted upper ends, acting as wedges, push the extremities of the plate-spring 1 toward each other and retract the studs m m until they clear the holes 1' 2' respectively, when the cylinder is unlocked and may be lifted up and taken out of its seat 1'.) In Fig. 10 the lug M is shown drawn down and the stud m retracted, as is also the case in Fig. 9, while the lug M is, in each of the illustrations, shown in its normal position with its end of the spring I close to the wall and the stud m protruding into the hole 2' All the remaining structure of the needle cylinder being substantially such as is either well known or else constituting the subjectmatter of aforesaid United States Patent No.

333,102, they are here passed by, merely referring to the fact that while Fig. 9 shows the summit of the needle-cylinder I capped by a row of sinkers I' of the general nature and character best adapted to work in combination with the remaining parts of the machine herein described, yet other sinkers adapted to work in conjunction with presser- Observed, first, that the dot-and-dash line of Fig. 11 indicates the division of the ca1n-cylinder into what may be called the knitting and the idle zones. Of these the latter, the idle-zone, (designated as B is commonly known as the needle rest or seat, along which the heels or offset lower ends of the needles normally slide in continual undisturbed succession one after another as they describe their course carried by their slots in the needle-cylinder. Said rest I form of a separate semicircular segment B adapted to repose, as shown in Figs. 13 and 14, with the stems of the screws b b" resting in the bottoms of their respective port-holes in the vertical shell of the cam-cylinder, and so B by its upper surface, serves normallyto connect into a continuous path the two ends of the actuating cam zone, (shown at n n in Fig. 12;) second,that into the half of the cam-cylinder H which lies between said termini n n, as shown in Fig. 12, there is compressed and adapted the entire needle-actuating cam system.

Save for the automatic actuating mechanisms combined therewith for the purpose of changing the length of the needles stroke, or of bringing into or out of action, as the case may be, the secondary devices for throwing in or out of gear individual needles, or possibly the somewhat unusually short central return-cam N,with its recessed lower extremity and loosely-pivoted switch-point n, said cam system is substantially composed, first, of the ordinary cam-path for reciprocating the needles normally during continuous tubular knitting; second, of other avenues or by-paths, (the approaches to which are controlled by the secondary cam-train,) into which certain of the needles heels are automatically delivered during the recipro cations of the needle-cylinder. Said by-paths are constituted by incorporating with the cams of the above-mentioned cam-path, first, pivoted needle-lifter tumblers 02. n acting in conjunction with fixed switch-cams N N for passing individual needles from the active to the non-active ranks; second, fixed outlying guard-cams N N for returning needles accidentally displaced to their normal level prior to their entering the actuating cam zone proper; third, automatically-movable downcast cam-lobes N N (best seen in Figs. 18 and 23) secured to the inner faces of the ends of their respective actuating-lever arms d d forming the auxiliary stitch-tightening device, and, fourth,on occasionto wit. ,when Fis swung up into action-dependent oscillatin g depressor-tumblers F F acting in conjunction with laterally-extending free-standing wings of the central fixed cam N to return non-acting needles into action, all of which devices, both in form and location, when associated as above referred to and as illustrated in the accompanying drawings, can be best taken up and explained during a consideration of their respective duties as they jointly or severally succeed and occur.

Therefore, passing now to the operation of the whole as above set forth and combined, it will be seen that the various parts in operation act as follows: The shipper being placed asin Fig. 1, guides, by means of the fork 5 an endless belt supplying motive power in the usual way to wheel XV, from which it is transmitted by shaft S to gearwheel V, which, by its intermeshing teeth, also revolves the smaller pinion-wheel V with a more rapid continuous circular motion. This motion, the machine being now supposed to be upon the point of beginning its duty of knitting a stocking, is transmitted to the shaft S as follows: The slider-disk V being at this stage of the operation in its normal positionbanked close against the side of the gear-wheel V, as shown in Fig. 1 and indicated in the dotted outline of the disk given in Fig.athe laterally-projecting stud P entering into its corresponding hole in the side of the gear V locks the two together radially and drives the shaft S by the feather s and the whole revolves together in the bearings 00 00* and drives, by means of the feather the second sliderclutch disk U", which, under the constraint of the fork u of the U- shaped slider-piece U is now held longitudinally near to the bearing 00 and has its clutchstud P free of the pinion-wheelU, which (U) being loose upon shaft S, so far as regards radial motion, rides idle. Its longitudinal relation to U is correctly maintained by the inward-pointing flanges of'the segmental clips of the fixed face-plate S (See Figs. 4 and P.) The shaft S being connected in this way, revolves continuously and carries with it the hand-wheel s and the bevel-gear 3 which latter, gearing with the miter-teeth'i, revolves the ann ularneedle-cylinder socket I and with it the cylinder which may have been secured thereto by the studs m a Said cylinder being equipped with needles as above mentioned, one of which is shown in Fig. 24, or with some other variety equally suitable, such as that shown in Letters Patent of the United States No. 333,102, granted to me on the 29th day of December, A. D. 1885, when thus continuously rotated, causes them to pass their heels successively along the upper surface of the cam-rest B which rest at this stage of the operation is in its lowest position, (shown in Fig. 13;) for the cam-wheel B, Fig. 14, being still at rest, presents a part of its continuous circular periphery incontact with the buffer end Z) of the rock-arm I), as shown in Fig. 14, thus permitting gravity or a spring, as shown in Fig. 14 at L to cause the leverarms 19 b together with the needle-rest-actuating bridle B, to occupy at this stage their corresponding lowest position. From the upper surface of B when in this position (also shown in Figs. 11 and 13) the needles heels moving to the right or left, according to the direction in which the cylinder I may be revolved, cross the line dividing the knittingzone from the idle-zone and pass on to and along the lifting-tumbler. n or or", as the case 7 may be, which tumblers are now both in their normal positionthat is to say, as they are 'to be placed preferably by the constructor on assembling the machine,viz. both as shown at n n in Fig. 23which is, in other words, lyin g so as to form a bridge or inclined way connectin g the upper surface of the cam-zone designated n n and the adjacent cam-surface of the downeast stitch-cams N or N and thence said needles feet pass successively-to and up one or other of said cams, as the case maybe if N in the path indicated in the dash-and-dot line of Fig. 23until they reach its summit, from which the angular motion of the needlecylinder swings them across the gap between said cam (say N and the central depressingcam N, under the lowest extremity of which they meet and swing the switch-point n from its normal (perpendicular) pendulous position about the pivot 12 until it occupies the position indicated by broken lines in said Fig. 23, (also indicated in the dotted outline designated n in Fig 12,) whereby the needles are forced downward as they are further swung onward toward the other stitch-cam N, (or N if the knitting be carried on in the opposite direction, in which case also the point n would assume the other dotted position, designated n in said Fig. 12.) Along said cam they then move, as is further indicated in the aforesaid dot-and-dash line of Fig. 23, until having cleared its lowest extremity they are swung across the gap between it and the adjoining ascending portion of the fixed cam N, prior to meeting which, the first of them, when it encounters the remaining lifter-tum bler (viz., either 91 or 01 also inclined inward and resting against its adjacent stitchcam as n rests 'on N in said Fig. 23,) causes this lifter to revolve upon its pivot and take the position shown in broken lines at n in Fig. 23, such position being allowed to either of these lifter-fingers by reason of the cam-wheel 0 being in its assembling position with its highest level 0 in contact with friction-roller 0, whereby lever c is swung upon its fulcrum S and the whisker c is 011 either hanc depressed toward the bottoms of the ports 0 0 and these ports being formed so as to extend sufficiently far down toward the table T allow said whiskersinwa1-dly-protruding ends to now he so low that the needles heels, passing from the active to the nonactive cam-zone, can, uninterruptedly, move outward over such non-active tumbler-via, one in the position shown at n in Fig. 23 but should a and n not actually he below the horizon of the upper surface N when thus turned outward the pressure of the needles heels passing and thrusting them downward toward the rest B I have found, is sufficient to raise the outer end of the lever c by crowding said whisker 0 still farther down toward the bottom of its port,and so force the back of such lifter-tumbler to the level of the needle-rest 13 along which the needles are next again to successively pass. The vertical throws rep- IIO resented in the dot-and-dash line of Fig. 23 thus administered to the needles constitute what is easily recognized as the ordinary wave motion necessary to be imparted to their hook-bearing upper ends (see the needle shown in Fig. 2%) to operate in conjunction with any of the ordinary bobbin-rests, bobbins, tension .and yarn-feeding devices with which the machine is presumably equipped; and when a tubular web of the prescribed length has been produced by their well-understood interaction to form the leg of the stocking the knitting operation of my improved machine then comes automatically to rest for a certain period by the intervention of pattern-wheels, and this as follows, viz: During every revolution of the belt-wheel WV (see Fig. 1) the tappet 10 has struck and swung the rocking lever w and thereby carried the pawls P P in an arc back and forth an equal number of times over the ratchetwheels \V V and as, at the outset of the knitting operation, these pawls are assembled so that the pawl P has its detent 10 in the oblique face of the upper end of the lug 10 free of the spring-catch to (see Figs. 7 and S) gravity then causes it to occupy substantially the position in which its companion pawl P and lug w are represented as 00011- pying in said Fig. '7. Now, while in said position the nose of the awl P en 'a iin the p D D O teeth of the idle ratohetwheel V drives said wheel by the space of, say, one tooth for each revolution of the shaft S; but said idle ratchet-wheel having now arrived at a point where one of its above-mentioned abnormallyhigh teeth of Fig. 7) meets the pawl P said tooth rotates the same through such an are upon its pivot that the upward extending lug 10 sliding its wedge-like upper surface under the edge of the plate-spring 10 lifts said spring until first the notch 10 of the lug w of the pawlP is disengaged; then, second, when said high tooth \V has passed from under, pawl P hooks itself up on said catch-spring 10 by engaging the downward-turned edge thereof with its own detent Meanwhile gravity acting upon pawl P drops it into action on the driving ratchetwheel XV, and the shaft S hitherto motionless, begins to receive from the pawl P with each revolution of the belt-wheel XV, an intermittent circular motion, whereby it will be seen that the wheels V are not only a means of communicating intermittent movements, but also in point of fact are patternwheels as well-that is to sayythe function of these fast and idler ratchet-Wheels is, in accordance with the pattern, to alternately and automatically put in motion or again to leave at rest the shaft S carrying the former or pattern wheels or secondary camtrain. For example, if the pattern of hose to be knit calls for a leg having five hundred and fifty rows of stitches a number of ratchetteeth equal to the number of impulses which the tappet iv delivers to the lever 10 during the operation of revolving the movable cylinder five hundred and fifty times is counted off upon the teeth of the idle ratchet-wheel. The count commences from the tooth initially registeringwith the pawl P ,and then a higher tooth is introduced. hen the back of this tooth is automatically brought by action of the tappet-lever and consequent advances of the idle ratchet-wheel WW underneath its pawl P it Will not only effect the throw-oft and latching out of gear of that pawl, as above described, but it will simultaneously release and bringinto operation the previously non-active pawl P and thus cause the tappet-lever through the medium of the fixed ratchet-wheel W to set the secondary cam-train in motion. This done, certain of the secondary cams operate,as hereinafter fully described, to modify the normal action of the machine, and then, as soon as these cam-wheels have been driven by the ratchet-wheel W through a sufficient arc of revolution to accomplish their present duty, the tappet having also brought said fixed ratchet-wheel at the same moment to a position where it presents a pattern or higher tooth than its ordinary series within range of the tappet-pawl P as it swings back to take anew actuating-stroke, then this tooth by lifting it higher than usual puts that pawl back out of gear; and locking it upon the tappet-lever spring-latch simultaneously for the coming stroke drops into gear upon the idle ratchet-wheel the other pawl P and this wheel recommencing from the high tooth which lately put it out of gear is driven idly while the pawl P counts off upon its periphery a tooth for each forward stroke of the tappetlever toward its own next higher tooth,which, in conformity with the pattern, is also contrived to be distant just as many teeth as there are strokes of the tappet to be made before the secondary cam-train shall be again required to act in any of its various functions but, as soon as that occurs, another highertooth of the idle ratchet-wheel meets its pawl P and a shift of the ratchet-pawls takes place automatically, and so on. By this means I accomplish the duty of actuating thesecondary cam-train only as is required in conformity to the pattern, and that by a very compact mechanical arrangement. By this meansviz., alternating the thrust of tappetlever 10 between a loose wheel, as and a wheel, as \V, which is fixed to the drive-shaft S of the secondary cam-train-I accomplish the duty of actuating said secondary camtrain only when, in conformity to the pattern, the same is required to be in action. It is, moreover, a very compact mechanical arrangement, towit: By it I am able to make intermittently-actuated cam-wheels of comparatively small diameter take the place of more cumbersome and practically continuously-actuated devices, of which sort of devices there is an illustration in Fig. 7 wherein, in place of cam-wheel B, there are placed, within range of a cam-ireading-lever end Z2,

such as is shown in Fig. 14, a cam 19* fixed at proper intervals to the face of an endless chain Z9 rove upon a sprocket-wheel B fixed to shaft S and for operatively connecting said cam-chain modification to the general driving parts of the machine a substantially continuous rotary driving mechanism is indicated in Fig. 7 by the outline of toothed wheel W and an actually continuous one is shown in the same view by the sprocket-wheels N 7200 and chain W connecting shafts S and S The rotation of the cam or pattern wheel A brings it from the position of having the lowest part in its peripheryviz., an -in contact with the bent arm a of the lever A into that of having the arm ct forced outward by the adjoining incline or cam which connects said lowest part a with the slightly higher circular portion, (designated a in Fig. 5.) This passage of the arm a from surface a to a forces the lever A to revolve horizontally through a small angle, upon its pivot, in the direction shown by the curved arrow near said pivot P in Fig. 6, and by said movement to thrust its disks a a against the abutment o and force the slider -rod S not only endwise through the lugs i 25 but outward toward the hand wheel .9 thereby compressing the springs Q and Q between their respective abutments-viz., Q between '0 and the adjoining face of the eye 29, and Q between '0 and the adjoining side of the eye The spring Q is also by this same motion of the rod S compressed between its abutment 4; and the adjoining end of the slider U and so forces said slider in the same outward direction as the rod S moves in. (See Fig. 1.) In addition the slider U by the sidewise drag of the straddling legs 1w on the flanges of the grooves 41 M, respectively, carries with it the disks V U along the shaft S and keys .5 5- respectively, and by so doing causes the stud- P to begin to be retracted from the hole 12 in the pinion V until, while it is still partially inserted therein, its further retraction is temporarily arrested by reason of the inwardlyturned tip j of the stationary finger J coming into contact with a part of the adjoining side of the larger flange of the said disk V and against this flange the tipj now continues to rub until the pin P which is still locked to and driven by the pinion V, turns the disk V so that the gap J comes into alignment with said tip j. Then as soon as that takes place the spring Q, pressing against its fixed abutment c forces the slider U still farther in the same outward direction until the disk V sliding its gap J over, finally envelops the finger j, thereby locking not only itself, but also, by the agency of the key 8 the shaft S from rotary motion. At the same time the complete releasing of the stud P from the hole 0 which takes place concurrently with and by virtue of said lateral thrust of the spring Q, permits the pinion V to run idly about the now motionless shaft S. Thus all parts which previously derived their motion (including the head H I, 850.) from shaft S come not only to rest, but also, as often as this part of the-operation may be repeated, to rest in precisely the same relative alignment; but, since the belt-wheel W is still revolving, the pawl P continuing in action, drives the secondary cam-train, and in it the cam-wheel B now comes into operationthat is to say, during this arrest of the knitting operation the cam 19, projecting from the wheelB, (see Fig. 14,) is revolved against the buffer 19 and causes it to rotate the shaft S through such an are that the arms 19 b (attached thereto) rise from the position shown in Figs. 2 and 14 until the screws bb (uniting the bridle B and the needle-rest B are forced upward to the tops of the ports 1) b, in which position they cause the needle-rest B and all the needles which may then be reposing their feet upon it to come above the active level of the cam-train in the camcylinder H-viz., to the non-active level designated by the dot-and-dash line in Fig. 21. The cam 11 is preferably of the form shown in profile in Fig. 1 lto wit, consisting of an easy inclinethe cam proper and a radial connecting-surface leading back to the otherwise continuous circular periphery of the wheel 13, whereby the buifer I), having once been acted upon and passed by said incline cam 11*, it immediately, under the action of gravity or the aforesaid spring L swings back into its normal position of contact with said circular periphery of B. Thereby the needle-rest B under the attachment of the screws 19 b is also dropped back into the position shown in Fig. 14; but the needles which were raised by it are maintained in the usual manner by the friction of the stitches and a compress-girdle encompassing their shafts in the ordinary way in the annular groove 1 of the needle-cylinder I (see Fig. 9) and remain for the time lifted out of gear. At the same time the aforesaid action of pawl P and ratchet-wheel W having brought the notch connecting the levels 0 and c of the camwheel C not only under but clear of the friction-roller c, has permitted gravity to drop said roller 0 from the previous position which it was maintained in on the high level 0 of the wheel C to the next lower one 0", and thereby lifting the whisker-bearing end 0 through a suflicient angle causes the inner ends of the whisker c to rise in the ports 0 e and .raise the recumbent lifter-tumblers, or rather that one of them which is then turned outward, as n in Fig. 23 is, so that it (and also its fellow, 91 when that one subse quentlybecomes turned into a corresponding prone position) is lifted at its free or swinging and notch-bearing extremity so far above the level of the normal needle-path (see n, Fig. 12) that. the heel of the first needle which swings along it in inward direction-viz. from N toward N"-may be caught in and engage with the same, to the end that as it is further swung onward by the needle-cylinder in its now reciprocating rotating motion said needle may be, first, deflected and carried in an upward arc until its heel is discharged (preferably while still ascending) upon the overlying inclined way formed by the slanting upper side of the fixed cam N whereby it is, second, shunted up into the non-active level above the cams,and,joining the ranks of those that had previously been placed in a similar condition by the above-described action of the sliding needle-rest B it also remains out of action for the time being. All of this operation, save the automatic seating, of either of the lifter-tumblers n or n is well understood and fully described in my aforesaid United States Patent No. 333,102. Then after said duty by the cams B and C the shaft S by a still further partial revolution, (see Fig. 5,) causes the highest level a of the wheel A to come opposite the arm a. In doing this the incline surface connecting the levels a and a, acting as a cam, again pushes said arm a farther outward from the shaft 5 and swings the lever A still farther in the direction indicated by the curved arrow in Fig. 6, andmakes the lever, in substantially the same way as it previously acted, shove the slider U with the parts connected thereto, not only in a continuation of the same path and direction which was previously given them until said disk V clears its gap J of the finger j, but also moves the other disk U so far toward the pinion U that the stud P having first come into contact with and banked against some part of the adjoining side of this pinion U, remains milling there in rubbing contact until the same has revolved sufficiently about the shaft S (upon which it had, up to this stage, ridden idly with a reciprocating circular motion imparted to it, as hereinafter set forth) to bring the hole 10 into registering alignment with the aforesaid stud P Then that stud entering therein, by means of the disk U and key 8 looks the pinion U to the shaft S, substantially as shown in Fig. 4c. The necessary additional lateral throw of the slider U requisite for the above-described entering of the stud P in hole a when the two are thus brought into alignment, is furnished the slider U by the spring Q thrusting against the abutment o which is, in its turn, banked by the slide-rod S forcing its other abutment t t o against the now stationary disks a a of the arm A.

Referring once more to the shaft S, it will be seen on inspecting Figs. 1 and 2 that it has, during every revolution of the belt wheel V, caused the rock-arm R to vibrate back and forth upon its pivot 19 by means of the 'crank s, pivot 1J knuckle s and pin p Said vibrating arm B, it will also be readily understood, has a varying angular velocity imparted to it by the connecting-rod s, to wit: One which is swiftest when said rock arm R is passing a line drawn vertically through its point of oscillation, (the center of the pivot p,) and slowest, just as'it either approaches or leaves the lateral limits of the circular are through which it swings; or, in other words, slowing to-its movements of reversal; and as the pivot 19 connects the upper end of said arm R by means of the knuckle r to the drag-link 0', said link has also been thereby reciprocated back and forth in curves a number of times equal to the revolutions described by said main driving-shaft S, by the pin p and caused the segmental toothed rack U to oscillate to and fro upon'its pivot P a similar number of times; and its teeth intermeshing with those of the pinionwheel U have imparted to it a reciprocating rotary motion of correspondingly varying angular velocity upon the shaft S. This, as aforesaid, has been merely an idle function while V was in the position relative to the slider U (shown in Fig. 1,) but which, on the coming into contact of the stud P and the side of said pinion U, has, as above described, served to first align said stud with the hole 0 and, second, when they were coupled together to then impart, by virtue of the disk U and key 3 the peculiar rotary motion which it now has to the shaft S, and by it through the miter-gears s and 2' to the needle-cylinder I. Moreover, at the time when the stud P enters the aforesaid hole a the original assembling of the various parts of the machine having been calculated so that the pinion U shall be at said moment intermeshed on the central portion of the segmental rack U, the first movement imparted to the cylinder I by the revolution of the crank s is to cause the needle-cylinder to take exactly one-half of a complete revolution (the number of teeth on the rack and pinion respectively being adapted to impart that much angular motion to such needle-cylinder by such a swinging from said central point of the rack to either end of its throw) and by this half-revolution to cause all the needles that were left (after the action of B in the active zone to move practically uninterruptedly outward over a needle-lifter tumbler in the latent position indicated by dotand-dash line at n in Fig. 23, and come momentarily to rest with their heels upon said needle-rest 13 From this position they pass, by the succeeding reciprocations of pinionwheel U, as above mentioned, to and fro through the cam system and lose their terminal needle with each passage of the cam until finally they arrive at the desired point, say when one-sixth of the whole number of needles with which the cylinder I may be equipped remainin action. Then the designated time for turning the heel having arrived,the wheel 0 further revolving causes the roller 0 to fall from the level 0 to c and assume the position shown in Fig. 15, in which the whisker c raises the lifter-tumblers points of repose sufficiently high to elevate their entire notch-bearing ends above the level in which the needles feet sweep along at n, as indicated at n in Fig. 23. This causes the first needle which meets with either of them thus elevated as said needle passes from the needle-rest B into the cam area of the cylinder H to swing said tumbler about its pivot and leave it in the position shown at n in Fig. 23that is to say, the tumblers are made to automatically reassume the primary function of bridges leading to their adjoining stitch-cams l 7 or N. This takes place without deflecting said first needle, which thus met the lifter, from its normal paththe dot-and-dash line of Fig. 23. Concurrently with this reversion to the normal arrangement of the cam system of the cylinder H the shaft S also brings the high level f of the cam F from under the frictionroller bearing end of the lever f and thereby rotating it upon the axle S raises f and swings the hinged flap F up into the position of contact with the external wall of cylinder H, as shown in Fig. 20, thereby bringing the upper ends F* and F thereof not only above and within the upper rim of said cylinder, but also causing the depressors F F to slide forward, and clearing the shelves 72, h under the influence of gravity, to come into range of such of the needles heels as are now in the nonactive level indicated in the dot-and-dash line in Fig. 2 These depressors thereupon, during the still continued reciprocations of the cylinder-head, begin and continue to act with their notch-bearing lower extremities, as follows, to wit: It is to be noted that these depressor-fingers (shown in Figs. 20 and 21) are substantially alike in shape, but assembled so that their beveled upper portions fall inward toward each other as rights and lefts that they both terminate upon their upper and unnotched extremities in rounded summits, while their inner or adjoining parts thence slope away in oblique faces F F extending downward approximately to the level of their points of suspension on the pivots 19 19 that otherwise their sides are substantially parallel and equidistant from said pivots; that im mediately above said pivots the set-springs g g are located, the inwardly-proj ecting free ends of which lie in range, respectively, of the arcs described by said depressor fingers rounded summits whenever they may be swung past them, the said springs g g being constructed of such a stiffness as to prevent either of said fingers passing under them by virtue of the momentum they may acquire in falling by themselves from, say, a horizontal to a perpendicular position in either direction. The objects of these arrangements are that F F can be so brought into action that while one of them lies inclined toward the direction in which the way-going series of non-active needles shall first approach them, yet the other then hangs straight downward, whereby it is obvious that they thus extend their notch-bearing lower extremities to different levels in the cam-cylinder H-to wit, that one which now banks its oblique face against its spring-catch, being substantially perpendicular, hangs deeper down; and, on

either hand, presents its straight fiat sides in the non-active levelthe dot-and-dash line of Fig. 21while its mate, F of said figure, banking the upper portion of its outer flat side against its catch-spring, (the length of both F and F being not only the same, but also proper for such purpose,) hangs at an angle calculated to bring its notch-bearing extremity into range of the non-active needles heels, the first of which heels, meeting said notch, is swept in a downward arc and delivered to the under side of the adjoining freestanding wing of the central depressorcam N, which leads said needle into the normal cam-path. Meanwhile, the n ext succeeding needles heel, meeting the side of this depressor-finger and swinging it farther 011- Ward, forces its summit under the overlying catch-spring. Then, when all the following needles have ridden under it, said depressor drops back and reposes with its oblique face against its catch-spring, and thereby said depressor-finger becomes, as it were, temporarily idlethat is to say, idle until after it be swung, by the return of the needle-cylinder, back to its active or angular position, substantially as its mate is now forced by what has become the leading non-active needle, when its heel .(meeting F similarly hanging straight down) bears against said depressors flat inner side, and rotating it under the overlying spring-catch q, suffers it, on the subsequent passage of the whole non-active series of needles heels from under it,'to drop back and repose turned outward with its notch lying in wait at its operative angle for the non-active needles return. S uch position is defined by virtue of the straight outer side of said depressor-finger then banking against (1 so that when these needles again return from the idle-zone by the reciprocations of the cylinder I they then cause each of these depressors to perform substantially the same act or duty which its mate went through on the last prior passage; and so on, alternately active and passive, the depressorfingers put back into gear single needles and thereby cause the fabric to turn and widen. Said widening is continued until such time as the machines head is brought by the revolution of the driving parts to a second period of rest. This occurs by the wheel A which is rotated by shaft S (a high tooth on wheel XV once more putting pawl P in action) now being brought so that the high level a, passing from in front of the lever a, allows it to be forced by the springs Q Q against the next adjoining lower level a and in consequence to allow said springs to retract the stud P from the hole 10 and then subsequently to hook the finger-tipj into the gap J, (substan tially in the converse way that said two parts were before brought into conjunction when a was thrust in the opposite direction by the lever A.) Said engagement now similarly locks the head driving mechanism in the predetermined and constant alignment, and al- 

